FR2500557A1 - TORSION DAMPER DEVICE, IN PARTICULAR CLUTCH FRICTION, IN PARTICULAR FOR A MOTOR VEHICLE - Google Patents

Abstract

THIS DEVICE INCLUDES PART AA HUB 10 AND HUB VEIL 11, PART BA GUIDE WASHER 12 AND FRICTION DISC 16, SPRINGS, SUCH AS 22, INTERPOSED CIRCUMFERENTIALLY BETWEEN THE SAID PARTS, AND AT LEAST ONE FRICTION WASHER 21 INTERPOSED AXIALLY BETWEEN THIS. FOLLOWING THE INVENTION, BETWEEN SUCH A RUBBER WASHER 31, WHICH IS IN CONTACT WITH PART B BY EACH OF ITS FACES IN THE EXAMPLE OF EMBODIMENT REPRESENTED, on the one hand, and PART A, on the other hand, IT PROVIDED FOR AT LEAST ONE LEG 38, WHICH, COMING FOR EXAMPLE FROM FRICTION WASHER 31, IS ENGAGED, WITH CIRCUMFERENTIAL CLEARANCE, IN A PASSAGE 39 PROVIDED FOR THIS EFFECT IN PART A. APPLICATION IN PARTICULAR TO CLUTCH FRICTIONS, IN PARTICULAR FOR MOTOR VEHICLES.

Description

The present invention relates generally to the devices

  torsion dampers of the kind comprising at least two coaxial parts, one exciting, the other excited, rotatably mounted relative to each other within the limits of a determined angular deflection and circumferentially interposed elastic means between

said parts.

  As is known, such a damping device of

  twisting between usually in the constitution of a

  clutch, in particular for a motor vehicle, one of its rotary parts then carrying a friction disc intended to be secured in rotation with a first shaft, in practice a driving shaft, the output shaft of the motor in the case of a motor vehicle, and thus forming an exciting part, while the other of its rotary parts is carried by a hub intended to be secured in rotation with a second shaft, in practice a driven shaft, the shaft

  entry of a gearbox in the case of such a vehicle

  automobile, and thus forms an excited part.

  Such a device makes it possible to ensure a trans-

  controlled mission of the rotation torque applied to one of its rotating parts when the other is itself the object

  rotation torque, that is to say, to filter the vibra-

  likely to arise throughout the kinematic chain on which it is inserted,

  engine to the wheel shafts controlled in the case of a vehicle

automobile.

  Most often the elastic means interposed cir-

  conferring between the two rotating parts of such a torsion damping device usually comprise a

  plurality of springs, all of which extend substantially

  substantially at a circumference of the assembly, and which are each arranged partly in a housing formed in a first of said rotating parts, and partly in a housing formed in the second of said rotating parts

  arrangements being made for intervention by

  pes of these springs, during successive portions of the angular displacement between said rotating parts, for a modulated increase in a determined manner of the overall stiffness due to these springs, this stiffness in front of

  be relatively low for low-income couples

  angular deflection, and relatively strong for

  couples lev4s, at the end of said angular deflection.

  In practice, the disprsitions result from this that one of the rears in question is, for the rest configuration of the assembly, disposed without circumferential clearance in the corresponding housing of a first of the rotating parts, and with a circumferential clearance J1 for a first direction of rotation, said set, and J2 for the direction of

  rottion 'ppos, da1a the corresponding box of the deu-

xviii dpccessitespr! e otvc

  r.f .... time, and therefore for

  e ..:. ::::: .- I? :: fet, its entry, nor actiea 1 -'iri: erv nrt ...: 1, e tmps, after absorption

neither ir & spondant.

  only some are capable of irterveni-. $ r's, which, in practice, are springs of rejuvenation low stiffness, while in 0C a second time. the effects of these springs of relatively low stiffness are added the effects of stiff springs

relatively strong.

  Jointly involve means of friction

  interposed between the two rotary parts concerned.

  These friction means usually comprise

  minus a friction washer, which is then rotated

  one of said rotary parts, for at least a range of angular displacement therebetween, and which, by

  at least one of its faces, is in contact with the other des-

said rotating parts.

  They aim to introduce a "hysteresis" effect

  in the evolution of the transmitted torque of one of the rotational parts

  to the other according to the angular displacement between them, that is to say to lead, for a given value of this deflection, a differentiation between the value of the corresponding torque for an increasing evolution of this

  couple, and the value of this couple for decreasing

  of the latter, which favors the absorption of energy.

  necessary for the desired filtration.

  A double problem must be overcome in the realization

  torsion damping devices of this type.

  First of all, it is desirable that the hysteresis

  troduced by the friction means implemented is different depending on the stiffness of the elastic means in action. In practice, this hysteresis can be important only when the elastic means in action have a strong

  stiffness, because the energy to be absorbed is then itself

  aunt. On the other hand, when the elastic means in action have only a low stiffness, and it is the case, as specified above, for the low torque values, it is preferable that the hysteresis developed by the means

  of friction is weak, under pain, other-

  "obliterate" or "stifle" these elastic means by

preventing their action.

  In addition, and jointly, the range of angular deflection during which are thus in action only elastic means of low stiffness, necessary for good noise filtration, said dead spots, which develop at the idle speed of the when the engine is stationary, the gearbox in neutral, can not generally be as extensive as it is desired because of the extension of such a range. stresses also the imperatives of mechanical construction and congestion of the damping device of

  concerned in which the place circularly circulates

  available, necessary for such an extension, is inevitable-

  limited by the fact that, apart from the idling speed for which they are so provided, these elastic means of low stiffness, are at the origin, with each momentary release of the accelerator pedal, and / or at each change of regime, an uncomfortable "sway" effect.

  In practice, however, for idling, and 2

  be constant with the temperature the amplitude of the oscilla-

  of the exciting rotating part, the oscillations cor-

  corresponding parts of the excited part develop on either side of an average position which does not correspond to a zero angular displacement between said parts, a pair

  parasite, called a drag couple, remaining on the contrary

  these parts and leading to the existence between them

  a non-zero angular deflection.

  Ge couple of drag, which is relatively important to

  cold, decreases with temperature.

  In practice, only a portion of the debate range

  angle corresponding to the elastic means of low stiffness is actually -used only for the oscillations of

  the exciting part to idle speed.

  But, it results from the existing drag torque while the implantation of this portion in this range varies.

with the temperature.

  If this drag torque is large enough, and

  this is the cold case, and if, for the reasons set out above,

  above, the extension of the range of angular displacement corresponding to the elastic means of low stiffness is limited, it may happen that, at idle speed, the oscillations of the excited portion lead it to come into contact with the elastic means of strong stiffness whose entry into action is normally provided only for the

  next range of said angular deflection.

  The sudden increase of stiffness intervening then

  not be the cause of a retrograde rebound.

  accelerated portion of the excited portion, which leads it to struggle untimely not only on a portion of the range of angular deflection corresponding to the

  resilient means of low stiffness, following oscilla-

  tions simply induced by those of the exciting part, but over the whole of this range, by successive twists at the ends of the latter, with production of a

specific noise accentuated.

  The present invention generally relates to a provision making it possible, very simply, to

  to overcome the consequences of such a rebound and lead

  in addition to other advantages.

  More specifically, the subject of the present invention is a torsion damping device, in particular a clutch friction device, in particular for a motor vehicle, of the type comprising at least those coaxial parts rotatably mounted, one Far and the other in the lirites of a determined angular displacement, elastic means interferentie between said rotating parts, and friction means interposed therebetween said elastic means including at least one spring, which extends substantially tangentially to a circumference of the together, and which for the configuration of reros of said assembly is arranged in part, without circumferential clearance, in a housing formed in a first

  rotating parts, and partly, with a circumstantial

  J1 for a direction of rotation of said assembly, and J2 for the opposite direction, in a housing formed in the second of said rotating parts, and said means for

  friction comprising at least one friction washer.

  which, by at least one of its faces, is in contact with a

  which of the two rotating parts, this device

  torsion weaver being characterized in that between

  the friction washer and the other of said rotating parts

  a leg, which comes from any of the elements formed by said friction washer and

  said other rotating part, and circumferential development

  LI, is engaged in a passage, such as window or notch, circumferential development L2,

  the other of those elements, the values of the circumferential

  J1, J2 and circumferential developments L1, L2, measured angularly, such that the difference [(Ji + J2) - (L2 - Li) J is between 0 and 5,

and preferably between 1 and 5.

  Thus, such a friction washer does not come into play.

  in action when, in the sense of rotation,

  born, the date associated with it is in abeyance against the ex-

  circumferential tremity of the reassurance in

she is engaged.

  The friction washer according to the invention, which has remained until it is inactive, and which thus has not until it obliterate the normal play of the elastic means of low stiffness, then systematically adds its effects to the other friction means jointly used. in the torsion damping device concerned, preferably introducing a friction torque multiple of that d, so that, in the case of a rebound of the excited portion relative to the exciting portion under the conditions set out above, it minimizes the consequences

  of such a rebound, ensuring a cushioning

accelerated process of it.

  In practice, by construction, and taking into account

  applications, the difference (L2 - L1) is chosen

  it is sufficient for the stabilized ring to prevent the ring from contacting the vocnion, whatever the temperature, so that it leaves a free

  in the second stiffness, for the filtz.

  The difference is that the difference (L2 - L1) is specified

l ......... '- J2) - (L2 - LI)

  the effective cost of accelerated depreciation.

  d of a possible rebound of the excited part vis-à-

  screw the exciting part, by the absorption energy that supplies, but only then, the washer of friction

according to the invention.

  In addition, the friction washer according to the invention is also mounted freely sliding around

  the axis of the whole, his intervention is advantageous

  without any concomitant compression of any particular elastic means capable of subsequently restoring the energy stored during

  such a compression, so that the unilateral movement

  temporary moment of this friction washer for a direction of evolution of the displacement between the two rotating parts

  concerned, does not necessarily imply the elastic return

  tick of this friction washer & its initial position

  when the direction of evolution of said deflection is reversed.

  On the contrary, the instantaneous position of the friction washer according to the invention results from the conditions

  previous operation, and is therefore any.

  However, regardless of this position, the friction washer according to the invention constitutes by itself a - 7 -

  absorption energy reserve whose entry into action does not

  advantageously, if necessary, without

  Damage to the normal operating conditions of the

  appears. The characteristics and advantages of the invention

  will also emerge from the following description.

  For example, with reference to the schematic drawings

  1 in which is a partial elevational view, along the arrow 1 of Figure 2, and with two local detachments, a torsion damping device according to the invention; Figure 2 is an axial sectional view along the broken line II-II of Figure 1; Figure 3 is an elevational view of the hub web that includes the torsion damping device, shown in isolation; FIG. 4 is an elevational view of the friction washer that also comprises according to the invention this

  torsion damping device, this friction washer

  being represented in isolation;

  FIG. 5 is a view in axial section of this ron-

  friction line, along the line V-V of Figure 4

  FIG. 6 is a diagram illustrating the function

  torsion damping device according to the invention.

tion;

  Figure 7 shows part of Figure 2 and relates to

  an alternative embodiment; FIG. 4 also shows part of FIG. 2 and relates to another embodiment variant;

  FIG. 9 is a partial cross-sectional view of

  the embodiment of this embodiment, along the line IX-IX of Figure E; Figure 10 is a view partly showing that of Figure 2 and relates to another embodiment; Figure 11 also shows part of that of Figure 2 and relates to another embodiment;

  Figure 12 is a partial cross-sectional view

  the embodiment of this embodiment, along the line XII-XII of Figure 11; FIG. 13 partially repeats that of FIG. 11 and relates to an alternative embodiment; Figure 14 also partially replicates that of Figure 11 and relates to another embodiment; Figures 15, 16 are views respectively similar to those of Figures 11, 12 and relate to another alternative embodiment; Figure 17 shows in part that of Figure 2 and relates to another embodiment;

  FIG. 18 is a partial cross-sectional view of

  dirty of this embodiment, along the line XVIII-XVIII of Figure 1? Figure 19 is partly that of Figure 2 and relates to another embodiment;

  FIGS. 20 and 21 are views respectively of

  to those of Figures 1 and 2 and relate to a. another variant embodiment;

  FIG. 22 is, on a larger scale, a partial view of

  axial section of this embodiment variant,

  along line XXII-XXII of Figure 20 *.

  These figures illustrate by way of example the application of the invention to the production of a clutch friction

  with damper hub for a motor vehicle.

  This clutch friction comprises in a generally

  In the exemplary embodiment shown, two parts

  coaxial assemblies rotatably mounted relative to one another

  within the limits of a defined angular deflection.

  Thus, there is first of all a first part A comprising

  both, in the exemplary embodiment shown, a hub 10 which, internally, is splined, for its rotational connection to a shaft, in practice a driven shaft, the input shaft of the gearbox of the vehicle concerned, and which, externally, radially projecting, in its central zone, a hub web 11 which is integral in rotation; for example, and as shown, this veiled hub, which is shown in isolation in FIG. 3, is

  crimped onto the hub 10 according to a technique

  which, well known in itself, will not be detailed here, but it may as well be a hubcap of a single

holding with the hub 10.

  Then there is a second part B with, in

  the embodiment shown, two washers of guiding

  12, which extend transversely to the axis

  S of the hub 10, on either side of the hub web 11, to be dis-

  of the latter, and which are connected to one another from place to place by axial spacers 13 traversing with clearance passages 14 provided for this purpose in the hub web 11, at the periphery thereof ; in practice, both

  guide washers are identical to each other.

  The second rotating part B further comprises a friction disc 16, which is secured in rotation to the guide washers 12, in contact with one of these, by the same axial spacers 13 which connect to each other.

these guide washers 12.

  At the inner periphery of the guide washer 12 to which is joined the friction disc 16 is disposed a bearing 17, which is interposed between the hub 10 and the guide washer 12, and which is wedged in rotation

PO on this one.

  In the embodiment shown in the figures it has radially projecting for this purpose, from place to place, bosses 1E by which it is engaged in notches 19 arranged in a manner complementary to the

  inner periphery of the guide washer 12.

  In addition, in the embodiment shown, the bearing 17 has transversely, parallel to the

  euidage ring 12 concerned, but at a distance from this

  ci, a radial collar 20 which is in contact with the

hub sail 11.

  Between the rotating parts A, B are interposed cir-

  conferring elastic means.

  These are divided into several levels of means

  elastics of different stiffness.

  First there is a first level, or floor, of

relatively lower stiffness.

  In the exemplary embodiments shown, the models

  elastic yens of this first level of stiffness comprise

  two springs 21 yes, in substantially diametrical positions-

- 10 -

  relative to each other, extend the one and the other noticeably tangentially C a circumference of the assembly, and which are each individually arranged for rarity in a housing 21A formed in the part rotary Ai and it is in practice a window made in the veil

  of hub 1l that includes this rotating part A, and for par-

  in a housing 21B formed in the rotating part B, and it is actually practical windows provided for this purpose in the guide washers 12 that includes this rotating part B, corresponding to one of these guide washers 12 to the other.

  For the rest configuration of the assembly, such as

  In FIG. 1, the springs 21 are engaged without play Circfrn'e !. trt in their home 21A only in their logu

  1, 2, where they have similar

  :) we are doing so, Sbuliant a var-aut2 of unrepresented realization, the; In other words, the housings 21B are inconferentially less in the said first receptacle than in the other direction.

  meaning that in the other, from a diametrical median plane cor-

  mun; in such a case and in a manner known per se, the springs

  2! 1 mounted in opposition, one relaxing when the other

  to be compressed, and vice versa.

  P5 Then there is a second level of elastic means

of relatively greater stiffness.

  In the exemplary embodiment described, it shgit, as pre-

  ceded, springs <S, 2 extending substantially tangentially

  to a circumference of the enseeible, the same for the springs 21, and arranged for part in dwellings 22A 22'A formed in the rotating partA and partly in housings

  22B, 22 'forms in the rotating partB, according to

  similar to those described above.

  However, for the rest configuration of the set,

  a5 and while the springs 22, 2r are engaged without circling

  in their dwellings 22B, 22'B of the Roman part

  tative B, there is a circumferential clearance between each of the circumferential ends of these springs and the wafer

  corresponding to housing 2L, 22'A of the rotating part

_ 11 _

  tive A in which they are also arranged.

  For a "pull" operation of the whole, such

  that, for example, indicated by the arrow F in FIG.

  ie for an operation of said set corresponding to an increasing evolution of the torque between the two rotating parts A, B which constitute it, this circumferential clearance has the value JI for the springs 22, which are two in number in the example of embodiment shown, being located in substantially diametrically opposite positions with respect to each other, and J'1 for the springs 22 ', which are also two in the embodiment example

  represented, being arranged in substantially di-

  contrasting each other, each

  re springs 22, 2c 'alternating with the springs 21.

  For a "retro" operation of the whole, that means

  that is to say for an operation corresponding to a decreasing evolution of the torque between the two rotating parts A, B, the circumferential clearance between the springs 22, _2 'and their housings 22B, 22'B has the value J2 for the springs 22 and the

I2 value for 22 'springs.

  In the exemplary embodiment shown, the game JI, on the one hand, and the game J'l, on the other hand are lower, respectively, to the game J2, on the one hand, and to the game J2idother

  share; alternatively, they could be equal.

  In addition, in the exemplary embodiment shown, the

  games JI, J2 associated with the springs 22 are respectively in-

  I1, J'2 associated with the springs 22 '.

  In use, and because of these circumferential clearances, the entry into action of the springs 22, 22 'is delayed and staggered, as illustrated in the diagram of FIG. 6.

  On this diagram we have taken as the abscissa the debate-

  angularly D between the rotating parts A, B, and on the ordinate the torque C transmitted between these rotating parts

A, B.

  Where, for a drawing operation of the whole,

  a pair C is applied to part B for example, which is therefore an exciting part, for transmission to part A, which therefore constitutes an excited part,

- 12 -

  springs of relatively lower stiffness 21 are first

the only ones to intervene.

  The representative curve of this first phase of

  is a straight line I whose slope is proportionally

  This first phase of operation continues until, for a value D1 of the angular deflection,

  the circumferential clearance J1 associated with the springs 22 is ab-

  sorbed. From this moment, the springs 22 come into

  action and add their effects to those of the springs 21.

  The representative curve of this second phase of operation is therefore a line II with a slope greater than

* that of the previous line I.

  This second phase of operation continues until, for a value D2 of the angular displacement,

  the game J'1 associated with the springs 22 'is in turn absorbed.

  The springs 22 'in turn come into action and

  therefore add their effects to those of 22 and 21.

  The representative curve of this third phase of operation is therefore a straight line III of higher slope

  to that of the previous line II.

  This third phase of operation continues itself until, for a value D3 of the deflection

  angular, there is a positive training of the

  Tative A by the rotating part B, or that all or part of the springs 21, 22, 22 'come to contiguous turns, or that the axial spacers 13 abut against the

  corresponding slice of the passage 14 through which they pass.

  For a retro operation of the whole, a pro-

  inverse converse to that described above develops, for successive values of the angular deflection D'1, D'2

and D'3.

  Thus, overall, for low torque values, only the springs of relatively lower stiffness 21 intervene, for a range P of the angular deflection

  positive angular deflection D1 has an annual deflection

  gular negative of 1 and such that P = JI + J2.

  In the above, account has not been taken of

- 13 -

  friction, which introduce into the functioning of

  overall a 'hysteresis' effect, that is to say a difference

  for the same value of the angular deflection,

  between the value of the torque transmitted between the rotational parts

  tives A, B for an increasing evolution of this pair and the value of this same pair for a decreasing evolution of it. In addition to inevitable internal friction, friction means are specifically interposed 2 this effect between the rotating parts A, B, for damping oscillations and vibrations, and therefore noise, including noise developing in neutral vehicle

stopped.

  These friction means usually comprise one or more friction washers which, by at least one of their faces, are in contact with any one of the two rotary parts A, B, and which, for all or part of the angular displacement between these, are driven enrotation with the other of said rotating parts A, B. By friction washer is meant here as well as a simple free washer, in any material, chosen however for its qualities of friction, that all constituted by an appropriately applied application washer and friction lining, by adhesive bonding

  example, on such an application washer.

  In the embodiments illustrated by the

  gures, two friction washers 30, 31 are

work, in association.

  The first, the friction washer 30, intervenes

  a first side of the hub web 11, namely, in the example

  embodiment shown in FIGS. 1 to 6, on the side of

  this hub veil 1I opposite the friction disc 1c.

  In this embodiment, it is constituted

  an application washer 32, which, disposed between the

  the hub 11 and the guide ring 12 close, is

  rotated thereon by axial tabs 33 enga-

  for this purpose in passages Y4 of this guide ring 12, and which, on the side of the hub web 11, carries a

  Friction liner 35 in contact therewith.

- 14 -

  The second friction washer, 1 intervenes on the other side of the hub web 11, and therefore, in the embodiment shown in FIGS. 1 to 6, from the side of the hub

friction disc i6.

  In practice, in this embodiment, this

  3i friction washer is constituted by a simple ron-

  delle, and this one, whose external diameter is superior

  to that of the friction washer 30, is axially inserted

  between the radial flange 20 on the one hand

  1? and on the other hand the web of the friction disk 16 solidi-

  rotatiou dice the guide ring 12 close, this web extending to the bearing 17 in this embodiment; in case this veil -rie is not prolonged

  to the re ... er r1 {.. rondel9 de frotterent 31 is direc

  Contact with the guide ring 12 near.

  -. s!, u.r_.u! ' 5.'invention, between this -l'le of pet +? ", I year at least 1 of its laces, and prat; n <, Mer Each of it in the example

  shown, is in contact with the rotating part

  B, on the one hand, and the rotating part A, on the other hand, there is provided at least one axial wall 38, which, resulting from anelelement of the elements formed by the friction washer 31 and the rotating part A , is engaged with play in a

  passage 59 of the other of said elements.

  In the exemplary embodiment represented on the

  gures I to 6, two axial tabs 38 are provided, and those are derived from the friction washer 51, figures

2, 4 and 5.

  These legs 58 are substantially arranged in positions

  diametrically opposite one another.

  Together, the passages 59 in which they are engaged are formed by notches provided in the

  the veil of moeu11a] abas des fe] beings 22A that presents this

  for the housing of the springs 22.

  According to the invention, the tabs 38E each having a circumferential development L1, and the housings 9 in which they are engaged each having a development

  the circumferential value L2, the values of these developments circum-

  LI, L2 and Circumferential Games Ji, J2

_ 15 _

  associated with the 2PA springs measured anrularily, are such that the difference [(J1 + J2) - (L2 - Lli is included

  between 0 and 5, and preferably between 1 and 5.

  In the usual way, elastic means with axial action are also associated with friction washers.

30, 31.

  In the exemplary embodiment shown, it is a corrugated washer -.0, of the type sold under the name "ONDUFLEX" for example, interposed between the friction washer 30 and the guide washer 12 on

  which it is locked in rotation.

  Because, thus locked in rotation on a guide ring 12, it is further maintained in application against the hub web 11, the friction washer 30 has its effects throughout the angular movement between the rotating parts A, B. It is the same, on the other side of the hub, for the radial flange 20 of the bearing 17, this radial flange being wedged in rotation on the corresponding guide washer 12 P0 while being maintained in application against

the hub veil 11.

  On the other hand, provided that these axial tabs 38

  remain at a distance from the corresponding tranches of the

  crusts 39 of the hub veil 11 that they pass through, the rim

  Friction 31 according to the invention remains without effect.

  It is in fact driven by the rotating part B between two elements of which it is inserted,

  without relative displacement with respect to these elements.

  However, when, for one direction of rotation or another, these axial tabs 58 abut against the corresponding edge of the indentations 39 through which they pass, it is located by these axial tabs 38, rotated

  with the hub web 11, for the direction of rotation concerned.

  Tour as much as this direction of rotation remains the same, that is to say rour as much as the direction of evolution of the couple remains the same, it then occurs a relative displacement, with a concomitant development of friction, between, d on the one hand, the friction washer 51, and, on the other hand, the two elements of the rotating part B between which it

- 16 -

  is inserted, the friction washer 31 intervening then

  beforehand by each of its faces.

  Therefore, by adding its effects to those of the friction washer 30 and the radial collar 20 of the bearing 17, it minimizes the consequences of a possible rebound.

  of the excited rotating part A with respect to the rotational part

exciting tense B.

  Moreover, since it is mounted freely

  around the axis of the whole, his intervention

  advantageously without concomitantly

  compression of any particular elastic means likely to restore the stored energy later

during such compression.

  Preferably, the conditions are such that the couple

  of friction due to the single friction washer 31

  the invention is a multiple of that due to the other

  friction means already in action; in the example of

  illustrated in Figures 1 to 6, this multiple is

for example between 2 and 5.

  Such a relationship between the friction pairs in question can be found on the corresponding diagram.

(not shown)

  In the embodiment variant illustrated by FIG.

  7, the friction washer 31 is disposed on the same side as the washer 32, constituting the friction washer 30 between the latter and the spring washer 40; moreover, in this variant, the housing 59 through which each axial lug 38 of the friction washer 31 is formed by a window of the hub veil

  It's independent of windows 22 & of it.

  It is thus possible to choose the outer diameter of the friction washer 31, according to the particular applications envisaged, this diameter therefore being, if desired, smaller or larger than that of the washer of

  friction 30; preferably, however, and as

felt, it is equal to this one.

  it should be noted that, for the same angular deflection, the more the passage 30 of the hub web 11 is close to the axis of the assembly and the less there is material to be removed at this point.

- 17 -

hub sail 11.

  It should also be noted that it is possible to

  staggered, with the guide ring 12 concerned and the friction washers 0,, 1 a pre-assembled assembly, the tabs 533 of the application washer 32 constituting the

  friction washer being, for example, folded to this effect.

  fet beyond the guide ring 12.

  The constructive arrangements of the forms of

  of Figures E to 10 are substantially the same as those

  the described with reference to Figure 7, but in addition, the friction washer 31 is inserted axially ertre

  two washers 32, 42.

  The first, the application washer 32, is, as

  previously, in contact with the hub web 11,

  either through a friction lining

  suitably reported on it or a washer of

  free, and is linked in rotation to the washer of

  guide 12 close by axial tabs 33, as previously

is lying.

  The second, the application washer 42, is

  between the friction washer 31 and the spring washer

  40 and is rotated to the first washer of

32.

  For example, Figures 5 and 9, it shows as much

  recesses 43, in practice windows, as shown in FIG.

  té, that the application washer 32 has axial tabs 33, and, by its recesses 45, it is engaged without

  play on said axial legs 53 of this washer of application

32.

  Alternatively, Figure 10, it itself has axial lugs 44 engaged without play in recesses 45

  of the guide ring 12 near.

  anyway, and as for the form of realization

  illustrated in FIGS. 1 to 6, the friction washer

  31 is then in contact with the rotating part B by

each of its faces.

  It is the same in other variants of reali-

described below.

  In the embodiments illustrated by the

- 18 -

  There are 14 gures, the test disc 32 being connected in

  rotational part B and forming part of this

  here, the axial lugs 38E provided between the washer defrot-

  According to the invention, and such a rotating part B extend between said friction washer 31 and said

application washer 32.

  For this purpose, the passages: 9 with which cooperate

  the axial sections 38 are formed in the washer of application

32.

  This is for example, and as shown, simple embèèemeents or indentations formed at the outer periphery.

  of this applicator washer, FIG.

  In any case, no passage likely to

  The Cylindrical Stace of the Hub Veil 11 is Aloe

  1; pra: _ia u.a e, e conloinftoenret, the number of

  3ages prrat.ques.ua-1s the roudwheel 12 concerned.

  zeu.le 2-n gt; In these embodiments, the friction washer 5% according to the invention is in contact, not only with the hub web 11, by the uride of its faces, but

  still, by the other of its faces, an intercalated washer

  re 47, yes is inserted between it and the washer of applica-

  52, and which is connected in rotation to the rotary portion A. For example, Figure 11, the spacer washer 47 may, at its inner periphery, present% me last with

  which it is engaged, without play, with a set of teeth

  complementarily formed for this purpose on the hub 10.

  Alternatively, this spacer washer 47 can be crimped on the hub 10, or directly in contact with the veil

  hub i1, by a crimp bead 4E common.

  with this hub plate 11, FIG. 13, or at a distance from the hub web 11 by a separate crimping bead 49

  crimp bead 48 provided therefor, FIG. 14.

  it should be noted that, in this case, the friction washer

  31 may be a preassembled pre-assembled with the rotating part A. In the embodiment variant illustrated by the

  Figures 15 and 16, no washer application is pre-

  view, but, as for the previous embodiments,

- '19 -

  the friction washer 51 according to the invention is inserted

  gap between the hub web 11 and a spacer 47 wedged in rotation on the hub 10, for example following

  any of the preceding provisions.

  The spring washer 40 is directly in contact with this spacer washer 47, and the passages 39 in which are engaged the axial tabs 38 of the friction washer 31 are formed by windows provided for this purpose.

  effect in the guide ring 12 near.

  The embodiment illustrated in FIGS. 17 and 18 is in all respects analogous to that described above with reference to FIGS. 8 and 9, with the difference that the lugs provided between the friction washer 31 and the rotating part A are not 'extend more axially, as before,

but radially.

  In the exemplary embodiment shown, these lugs 38 thus extend radially to the inner periphery of the friction washer 31, the passages 359 with which they cooperate being formed on the outer periphery of the

hub 10.

  As best seen in Figure 1E, the pat-

  38 thus form a toothing, and the passages 39 together form a toothing similar to the previous, for

nesting with game with it.

  The embodiment variant illustrated in FIG. 19

  is in every respect analogous to the decreed embodiment of

  previously with reference to FIGS. 15 and 16, with the difference

  There is no elastic washer provided, at least on the side of the hub web. It involves the friction washer 31 according to the invention, the intermediate washer 4. associated with it being then directly in contact

  of the guide washer 12 nroche.

  The embodiment illustrated in FIGS. 20 to 22 is generally similar in overall terms to that described above with reference to FIGS.

  Figures I to 6, but with the following differences.

  The friction washer 31 according to the invention, yes, in this embodiment, is disposed on the side of the hub web opposite the friction disc 16, is

- 20 -

  axially inserted between the guide ring 12 correspon-

  dante and the radial collar 2c 'of a channel 17' which, cen-

  on said guide ring 12 by its outer periphery.

  C is a distance from the hub 1C, the latter having a recess 5u for this purpose, so that the only friction occurring on the side in question of the hub web is due to this.

friction washer 31.

  To this friction washer, it is associated, on the side of the friction disc 16, a friction washer 52, which

  is axially inserted between the guide washer corres-

  and the radial collar 20 of the bearing 17, and which,

  known manner, comprises on the one hand, at least one pat-

  the axial 53, and at least two radial arms 54; the paw

  axial 53 is engaged, possibly with play, in a pass-

  ge, in practice a notch 55, of the hub web, for the entry into action of the friction washer 52, and the radial arms 54 form a fork by which it is engaged on a spring 22, for its systematic recall in

  a median position of rest determined.

  Thus, to a friction washer 31 with a recess position

  indeterminate ros and random intervention is found in this

  case associated with a friction washer which, in a

  sic, has a determined rest position, and of which, in a classic way, the intervention is strictly

program.

  In the embodiment shown? both

  friction plates 31 and 52 thus implemented have the same

  diameter, which may allow uniqueness of manufacture.

  Finally, in the embodiment shown, these

  two washers are subjected to elastic means

  specific axial action ticks independently of each other. These are elastically deformable strips 50, which

  extend radially, and which, taking

  axial toises 15, at their end radially furthest from the axis of the assembly, act at their end

  radially closest to said axis, some on the adhesive

  radial strip 20 of the bearing 17, the others on the radial flange 20 'of the bearing 17', by soliciting these collars

- 21 -

  radial 2C, 2C 'towards the guide ring 12 near.

  Under the stress of these slats 50, the washers

  the rubs, 1, 52 are thus each indivi-

  secondly rinsed between on the one hand the guide washer 12 close, and, on the other hand, the radial flange 20, 20 '

of the bearing 17, 17 'corresponding.

  In this embodiment, the friction torque

  due to the friction washer according to the invention may be 5 to 15 times higher than that due to the other means of

  friction, and, for example, 10 times greater than this.

  As will have been noted, in all the embodiments described and shown, the axial tabs 33 and / or 38 are all arranged in a circumference of diameter less than that of the circumference on which

  there are the springs 21, 22, 22 '.

  But of course, the present invention is not limited to the embodiments described and shown, but encompasses any variant of execution and / or combination of

their various elements.

  In particular, the leg provided according to the invention

  between a friction washer and one of the rotating parts

  concerned, instead of coming from this puck of

  friction, may alternatively be derived from the

said rotating part.

  In addition, the clutch friction concerned, instead of having only two coaxial parts rotatably mounted

  relative to each other, may include, in a manner consistent with

  naked in itself, three coaxial parts rotatably mounted two to

* n0 two in relation to each other.

  The field of application of the invention is not limited to clutch friction only, but extends more generally to that of damping devices.

torsion.

  In addition, the provisions of the invention are not limited to only the first spring latch to intervene on the contrary, and in particular when two groups of springs

  of relatively low stiffness are implemented, they are

  wind, extend as well to the second trcupe of springs par - c .: exexrle; in this case, in the definition of invention jil

  and I2 are obviously to substitute for jl, D2 respectively.

- 23 -

REVESDICA-ION S

  1. torsion damping device, in particular friction of clutchaze, in particular for a motor vehicle, of the kind comprising at least two coaxial parts (A, B)

  mounted relative to each other in the limi-

  with a determined angular deflection, elastic means

  ticks interposed circumferentially between the said

  rotary elements, and friction means, interposed

  axially between them, said elastic means comprising

  at least one spring (22), which extends substantially

  gentially to a circumference of the assembly, and which, for the rest configuration of said assembly, is arranged for

  part, without circumferential clearance in a housing (22B)

  in a first (B) of the rotating parts, and for

  with a circumferential clearance J1 for a direction of rotation of said assembly and J2 for the opposite direction in a housing (22A) formed in the second (A) of said rotating parts,

  and said friction means having at least one ron-

  delle de friction (31) which, by at least one of its faces,

  is in contact with any one (A, B) of the two rotating parts

  tives (A, B), characterized in that between said washer

  of friction (31) and the other (B, A) of said rotating parts

  (A, B) there is provided a tab (38), which, resulting from a

  any of the elements formed by said friction washer

  (31) and said other rotating part (B, A) and

  circumferential development L1, is engaged in a

  wise (59) such as window or notch, of circumferential development L2, of the other of said elements, the values

  circumferential clearances J1, J2 and circumferential developments

  Conferences L1, L2, measured angularly, being such that the difference [(J1 + J2) - (L2 - L1 lies between O

  and 5, and preferably between 1 and 5.

  2. Device according to claim 1, characterized in that the friction torque due C the only washer of

  friction (31) is a multiple of that due to the other

friction yen.

  3. Torsion damping device according to the invention

  1, characterized in that said leg (3E) is

  sue of the friction washer (31).

- 24 -

  4. Torsion damping device according to the invention

  1, characterized in that said tab (38) is

  from said other rotating part (B, A).

  5. Torsion damping device according to one

  any of claims I to 4, characterized in that

  said tab (3E) extends axially.

  6. Torsion damping device according to one

  any of claims I to 4, characterized in that

  said tab (35E) extends radially.

  7. Torsion damping device according to one

  any of claims I to 6, characterized in that

  the friction washer (31) is in contact with any

  the two rotating parts (A, B) by each of its

these.

  8. Torsion damping device according to the invention

  6, and wherein one (A) of the rotating parts (A, B) has a hub (10), and the other (B) at least one guide ring (12), interposed between this hub (10) and this guide washer (12), a bearing (17, 17 ') which O20 is set in rotation on said guide washer (' 2), and which has transversely, parallel to the washer

  (12) a radial flange (20, 20 '), characterized in that

  in that the spring washer (31) is inserted in

  between the traditional affiliation (20) of the said

  bind (17) and secondly the guide washer (12) which is integral in rotation thereof or a solidarity part

  in rotation of said guide ring.

  9. Torsion damping device following the claim

  7, characterized in that the washer of friction

  (51) is inserted axially between two washers of appllica-

  tion (32, 42), of which a first (32) is, on the one hand, in contact with one (A) of the rotating parts (A, B) and, on the other hand,

  on the other hand, is linked in rotation to the other (B) of the

  tatives (h, B), and whose second (42) is rotatably connected to the first (52), either directly or by the other

rotating part (B).

  10. Torsion damping device according to the invention

  9, characterized in that for its rotational connection

  to said other rotating part (B) the first washer

- 25 -

  application (52) Has at least one axial lug (55), and, by a recess (45), such as window or notch, the second applicator washer (42) is engaged without

play on said leg (553).

  11. A torsion damping device according to claim 9, characterized in that, independently of one another, the first (52) and second (42) washers are each rotationally connected by at least one

  an axial lug (55,44) to said other rotatable portion (B).

  12. Torsion damping device according to the invention

  7, in which an applicator washer (52), which is subjected to elastic axial action means (40), is rotatably connected to one (B) of: rotary articulations (A, B), characterized in that the axial lug (53) provided between the friction washer (51) and one of the rotating parts (A, B) extends between said friction washer (51) and said applicator washer (32,

  15. Torsion damping device according to the invention

  7, characterized in that the friction washer (515 is in contact with an intermediate washer (47), which is inserted between it and the application washer (52), and which is rotatably connected to the other (A) rotating parts

(A, B).

  14. Torsion damping device according to the invention

  7, in which one (A) of the rotating parts

  (A, B) comprises a hub (10) and a hub web (11).

  lidar rotation of said hub (10), characterized in that

  the friction washer (31) is inserted between said

  the hub (11) and a spacer washer (7) connected in

rotation to said hub (10).

  15. Torsion damping device according to one of

  any of these claims I to 6, wherein one (A)

  rotary parts (A, B) comprise a hub (O10) and a hub web (11) integral in rotation with said hub (10) while the other (B) comprises at least one washer of

  guide (12) and an application washer (52) which,

  Axially actuated axial means (4C) bearing on said guide ring (2) is rotatably connected thereto, characterized in that the friction washer (31) is axially arranged between the puck

  Arplication (32) and the guide washer (12).

  16. Torsion damping device according to one

  any of claims 1 to 15 and wherein one of

  (Al of the rotating parts (A, B) comprises a hub (10) and a web of oyeu (1.) integral in rotation with said hub (10),

  characterized in that the friction washer (31)

  comes from a first side of the hub veil (11) in association with

  other means of friction occurring in the

  ] O side of said hub web (11).

  17. Torsion damping device according to one

  any of claims i to 16, characterized in that

  at the same time (i) it is associated with another

  tfro. t (52) who, in contact with one of the

  On the other hand, at least one tab aXiisa ax U-, -u salupa = sage (55) of the other desditer ars aa.d There are at least two arms

  as..ux Ta: -j o gSe on a spring (22).

  i8. Twisting mortiser device according to the claim

  clication 17, which is characterized by the fact that the washers

  (31, 52) are subjected to resilient action means

  axis specific, independently of each other.

  19. A torsion damping device according to claim 5, wherein one (A) of the rotating parts (A, 3) comprises a

  hub 0i0Oand a hub web (11il) secured thereto, while the other (B) comprises at least one guide washer (12 characterized in that the passage (39) in which is engaged the pat3e (38) is formed either in the hub web (ii) or in the guide washer 012) or in an application washer (2) which rotates on

  any of the rotating parts (A, B).